WO2012130304A1 - Roue satellite pour engrenage planétaire - Google Patents

Roue satellite pour engrenage planétaire Download PDF

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Publication number
WO2012130304A1
WO2012130304A1 PCT/EP2011/054952 EP2011054952W WO2012130304A1 WO 2012130304 A1 WO2012130304 A1 WO 2012130304A1 EP 2011054952 W EP2011054952 W EP 2011054952W WO 2012130304 A1 WO2012130304 A1 WO 2012130304A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing bush
planetary gear
planet
planet gear
gear
Prior art date
Application number
PCT/EP2011/054952
Other languages
German (de)
English (en)
Inventor
Wolfgang Müller
Stephanie MIßNER
Thomas Maier
Original Assignee
Alfred Kärcher Gmbh & Co. Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Alfred Kärcher Gmbh & Co. Kg filed Critical Alfred Kärcher Gmbh & Co. Kg
Priority to BR112013018724A priority Critical patent/BR112013018724A2/pt
Priority to PCT/EP2011/054952 priority patent/WO2012130304A1/fr
Priority to EP11712530.2A priority patent/EP2691673A1/fr
Priority to CN2011800698713A priority patent/CN103477122A/zh
Publication of WO2012130304A1 publication Critical patent/WO2012130304A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/06—Use of materials; Use of treatments of toothed members or worms to affect their intrinsic material properties
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/107—Grooves for generating pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
    • F16C2208/02—Plastics; Synthetic resins, e.g. rubbers comprising fillers, fibres
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
    • F16C2208/20—Thermoplastic resins
    • F16C2208/66—Acetals, e.g. polyoxymethylene [POM]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/20—Sliding surface consisting mainly of plastics
    • F16C33/201—Composition of the plastic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/06—Use of materials; Use of treatments of toothed members or worms to affect their intrinsic material properties
    • F16H2055/065—Moulded gears, e.g. inserts therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H2057/085—Bearings for orbital gears

Definitions

  • the invention relates to a planetary gear for a planetary gear with a bearing bushing for connection to a planet carrier of the planetary gear and a bearing bush surrounding the circumferential gear ring, which is made of plastic.
  • Planetary gears serve the transmission of force and movement between a drive shaft, for example a motor shaft, and an output shaft. They include a centrally located first gear, which is commonly referred to as a sun gear and which is coupled via a plurality of second gears, which are commonly referred to as planet gears, with an internally toothed ring gear.
  • the planet gears are rotatably supported on a planetary carrier of the planetary gear.
  • a plastic planetary gear is known with axially projecting bearing journals which are rotatably supported in bearing bores of the planet carrier.
  • a planetary gear is known in which the bearing bush is designed as a steel bushing for mounting the planetary gear, for example, on a needle bearing.
  • the steel bushing is surrounded by a ring gear, which is made of a high-strength, heat-resistant plastic.
  • Object of the present invention is to develop a planetary gear of the type mentioned in such a way that it is cheaper to produce and assemble.
  • This object is achieved according to the invention in a planetary gear of the type mentioned in that the bearing bush forms a slide bearing made of plastic and the sprocket is molded as a plastic molded part to the bearing bush.
  • the planetary gear according to the invention is characterized u. a. characterized in that both the bearing bush and the ring gear are made of plastic.
  • the bearing bush can be produced by injection molding.
  • the bearing bush can then be overmoulded by the plastic material of the sprocket. The entire production of the planetary gear can thus be done in two-component injection molding.
  • the bearing bush forms a plain bearing in the planetary gear according to the invention, so that the planetary gear can be placed for mounting on a journal of the planet carrier.
  • the bushing then slidably abuts the journal and is rotatable relative thereto.
  • the assembly of the planetary gear thus designed as well as its production very cost.
  • the planetary gear according to the invention has the advantage that the bearing bush and the ring gear can be optimized independently of each other to their respective functions.
  • the bearing bush meets the planetary gear the function of sliding bearing on the journal of the planet carrier and can be optimized in this regard, in particular by the choice of the bearing bush for use for use plastic.
  • the sprocket serves the toothing of the planetary gear with the internally toothed ring gear of the planetary gear and can be optimized for example by selecting the plastic material used for the production of the ring gear in terms of smoothness of the planetary gear and the mechanical strength. Also with regard to the respective required temperature resistance, the bearing bush and the ring gear can be optimized independently. In an advantageous embodiment of the invention, the bearing bush and the ring gear are made of composite materials based on the same base material. The use of the same base material for the sprocket and the bearing bush facilitates the production of the planetary gear, since the material properties of bearing bush and ring gear are similar due to the matching base material and therefore in particular changes in material properties due to thermal influences are easier compensated.
  • the bearing bush and the sprocket are each made of a composite material based on POM (Polyoxymethy- len).
  • the composite materials of the bearing bush and ring gear may differ from the additives and / or reinforcing materials and / or fillers used in addition to the POM.
  • a fiber-reinforced POM material can be used for the sprocket and for the bearing bush, a POM material can be used, the additives are mixed to improve the sliding properties.
  • Such additives are known to those skilled in the art and therefore require no further explanation in the present case.
  • the bearing bush and the ring gear are preferably rotatably connected to each other by means of positive locking elements.
  • You can, for example, be arranged between the outside of the bearing bush and the voltage applied to the outside of the bearing bush inside the ring gear positive locking elements, which counteract a rotation of the ring gear relative to the bearing bush.
  • the interlocking elements are conveniently integrally connected to the bearing bush or the ring gear.
  • the positive locking elements extend over the entire length of the bearing bush. Air pockets that may form during encapsulation of the bearing bush, thereby have no significant impairment of the security against rotation result, because such air pockets are locally limited and extend in the axial direction at best over parts of the bearing bush.
  • the tangential and / or radial expansion of the interlocking elements varies in the axial direction. Under tangential expansion of the interlocking elements is presently understood to be the width in the circumferential direction of the bearing bush.
  • the radial extent of the positive locking elements corresponds to their material thickness.
  • the tangential and / or radial expansion of the interlocking elements continuously changes in the axial direction.
  • the tangential and / or radial expansion of the interlocking elements continuously increases or decreases starting from a first end face of the bearing bush in the direction of the second end face of the bearing bush.
  • interlocking elements are identical and vary identically in their tangential and / or radial extent in the axial direction.
  • the interlocking elements are designed as ribs, which are provided by an outer surface of the La gerbuchse protrude.
  • the ribs can form in combination with the bearing bush a one-piece plastic molded part, which is encapsulated by the sprocket.
  • the width and / or height of the ribs, d. H. their tangential or radial expansion, can change continuously in the axial direction preferably. It can be provided, for example, that the ribs extend over the entire length of the bearing bush, wherein they have a smaller width and / or a smaller height in the region of a first end side of the bearing bush than in the region of the second end side of the bearing bush.
  • the planet wheels of a planetary gear are arranged in an oil sump.
  • the interface between the bearing bush and the ring gear in the transition region between the end faces of the bearing bush and the outer surface of the bearing bush is designed like a labyrinth.
  • the labyrinthine shape of the interface reduces the risk of oil getting in between the bushing and the sprocket.
  • the bearing bush has an axially projecting collar on each of its two end faces, which collar is undercut from an end-side end section of the toothed ring.
  • the ring gear has end sections projecting in the axial direction over the end faces of the bearing bush, wherein the inner diameter of the planet gear between the end faces of the bearing bush and the axially projecting end portions of the ring gear expanded suddenly.
  • the planetary gear according to the invention has a diameter jump in such a configuration in the region between the end faces of the bearing bush and the end portions of the ring gear. This diameter jump allows the provision of a lubricant reservoir, which extends in the radial direction between the end portions of the ring gear and the bearing journal of the planet carrier when using the planetary gear.
  • the planetary gear explained above is preferably used in motor-driven cleaning devices, in particular in high-pressure cleaning devices and floor cleaning devices.
  • the planetary gear can, for example, be arranged between a drive motor, preferably an electric motor, and a swash plate with the aid of which pistons of a pump of the high-pressure cleaning devices can be moved back and forth in the axial direction.
  • Such planetary gears are subject to a high mechanical load and also a high temperature load. It has been found that higher temperatures can be realized in the planetary gear by using planet gears of the type described above, without the planetary gear is impaired.
  • Figure 1 a perspective view of a planetary gear according to the invention
  • Figure 2 is a perspective view of the planetary gear of Figure 1 in the manner of an exploded view
  • Figure 3 is a sectional view of the planetary gear along the line 3-3 in FIG.
  • FIG. 4 shows an enlarged view of detail X from FIG. 3;
  • Figure 5 a plan view of a bearing bush of the planetary gear of FIG.
  • Figure 6 a side view of the bearing bush in the direction of arrow A from
  • FIG. 5 is a diagrammatic representation of FIG. 5.
  • a planetary gear 10 is shown schematically, which is preferably used in a planetary gear of a motor-driven cleaning device, in particular a high pressure or floor cleaning device used. It is made entirely of plastic and comprises a sleeve-shaped bearing bush 12 and a toothed rim 14 which completely surrounds the bearing bush 12 in the circumferential direction and projects in the axial direction over a first end face 16 of the bearing bush 12 and over a second end face 18 of the bearing bush 12 , This becomes clear in particular from FIG.
  • the bushing 12 comprises a cylindrical shell 20, the shell inner surface of which forms a sliding surface 22 of the planetary gear 10 and on the outer circumferential surface 24 of which form-locking elements in the form of longitudinal ribs 26 protrude radially outwards.
  • longitudinal ribs 26 protrude radially outwards.
  • four identically designed longitudinal ribs 26 are used, which are arranged at a uniform angular distance from each other.
  • a first collar 28 of the bearing bush 12 protrudes in the axial direction beyond the first end face 16, and a second collar 30 protrudes in the axial direction beyond the second end face 18 of the bearing bush 12.
  • the two collars 28, 30 each comprise a plane end face 34 or 36 aligned perpendicular to the longitudinal axis 32 of the planetary gear 20, which merges via a conical transition surface 38 or 40 into the first end face 16 and the second end face 18 of the bearing bush 12.
  • the longitudinal ribs 26 extend over the entire length of the bearing bush 12 from the end face 34 of the first collar 28 to the end face 36 of the second collar 30. Starting from the end face 34, the longitudinal ribs 26 widen continuously up to the end surface 36, d. H. the mutually remote side surfaces 42, 44 of the longitudinal ribs 26 are aligned obliquely to each other. This becomes clear in particular from FIG.
  • the width of the longitudinal ribs 26 corresponds to the distance between the two side surfaces 42, 44, which increases continuously in the axial direction.
  • the width of the longitudinal ribs 26 corresponds to their tangential extent.
  • the ring gear 14 includes a first end portion 46 which protrudes in the axial direction over the first collar 28 of the bearing bush 12 and engages under the first collar 28 with an axially inwardly directed inner edge 48.
  • the ring gear 14 comprises a second end portion 50 which protrudes in the axial direction over the second collar 30 of the bearing bush 12 and the second collar 30 engages under an axially inwardly directed inner edge 52.
  • the inner diameters of the inner edges 48 and 52 are selected to be identical and larger than the inner diameter of the bearing bush 12.
  • the two collars 28, 30 give the interface between the bearing bush 12 and the ring gear 14 in the transition regions between the end faces 16 and 18 and the outer circumferential surface 24 a labyrinth-like shape.
  • the bearing bush 12 is produced with the longitudinal ribs 26 as a first one-piece plastic molded part in a first manufacturing step, which is encapsulated in a subsequent manufacturing step to form the ring gear 14 of flowable plastic material.
  • the bearing bush 12 is a composite based on POM (polyoxymethylene) are used, the additives for improving the sliding properties of the bearing bush 12 are mixed.
  • POM polyoxymethylene
  • the ring gear 14 is also a composite material based on POM (polyoxymethylene) is used, which are added to increase the mechanical stability reinforcing materials.
  • the ring gear 14 encloses the bearing bush 12 in the circumferential direction and protrudes in the axial direction on the bearing bush 12, wherein it engages under the collar 28 and 30 of the bearing bush 12.
  • the longitudinal ribs 28 of the bearing bush 12 form interlocking elements, which ensure a rotationally fixed connection between the bearing bush 12 and the ring gear 14.
  • the planet gear 10 can be placed on a bearing journal of a planet carrier, so that the sliding surface 22 of the bearing bush 12 slidably rests on the bearing journal.
  • a lubricant such as oil
  • the diameter steps 54 and 56 between the end faces 16, 18 and the inner edges 48 and 52 define a lubricant depot.
  • the labyrinthine configuration of the interface between the bearing bush 12 and the ring gear 14 in the transition regions between the end faces 16, 18 and the outer circumferential surface 24 here ensures that the lubricant can not penetrate between the bearing bush 12 and the ring gear 14.
  • the planetary gear 10 has a very high temperature resistance and is preferably used in planetary gearboxes of motor-driven cleaning devices, for example in high-pressure cleaning devices and floor cleaning devices.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Thermal Sciences (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)
  • Cleaning In General (AREA)

Abstract

L'invention concerne une roue satellite (10) pour un engrenage planétaire doté d'un coussinet (12) destiné à être raccordé à un porte-satellites de l'engrenage planétaire et d'une couronne dentée (14) en matière plastique entourant le coussinet (12) dans la direction circonférentielle. L'objet de l'invention est de perfectionner la roue satellite de sorte qu'elle puisse être fabriquée et montée de manière économique. A cet effet, le coussinet (12) forme un palier lisse en matière plastique et la couronne dentée (14) est formée sur le coussinet (12) en tant que pièce moulée en matière plastique. L'invention concerne en outre l'utilisation d'une roue satellite de ce type pour un engrenage planétaire d'un appareil de nettoyage à entraînement moteur.
PCT/EP2011/054952 2011-03-30 2011-03-30 Roue satellite pour engrenage planétaire WO2012130304A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
BR112013018724A BR112013018724A2 (pt) 2011-03-30 2011-03-30 roda planetária para uma engrenagem planetária
PCT/EP2011/054952 WO2012130304A1 (fr) 2011-03-30 2011-03-30 Roue satellite pour engrenage planétaire
EP11712530.2A EP2691673A1 (fr) 2011-03-30 2011-03-30 Roue satellite pour engrenage planétaire
CN2011800698713A CN103477122A (zh) 2011-03-30 2011-03-30 用于行星传动装置的行星齿轮

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2011/054952 WO2012130304A1 (fr) 2011-03-30 2011-03-30 Roue satellite pour engrenage planétaire

Publications (1)

Publication Number Publication Date
WO2012130304A1 true WO2012130304A1 (fr) 2012-10-04

Family

ID=44625693

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/054952 WO2012130304A1 (fr) 2011-03-30 2011-03-30 Roue satellite pour engrenage planétaire

Country Status (4)

Country Link
EP (1) EP2691673A1 (fr)
CN (1) CN103477122A (fr)
BR (1) BR112013018724A2 (fr)
WO (1) WO2012130304A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014208800A1 (de) * 2014-05-09 2015-11-12 Schaeffler Technologies AG & Co. KG Kunststoffplanetenrad mit eingespritztem Lager sowie Planetengetriebe
WO2016066745A3 (fr) * 2014-10-29 2016-06-23 Gwf Messsysteme Ag Roue et procédé de fabrication de cette roue
CN109695697A (zh) * 2019-01-25 2019-04-30 上海创率复合材料有限公司 齿轮及齿轮制造方法
US20200088284A1 (en) * 2018-09-17 2020-03-19 Borgwarner Inc. Gear assembly having a gear comprising a first polymer and a bushing comprising a second polymer
WO2021069186A1 (fr) * 2019-10-09 2021-04-15 Rolls-Royce Deutschland Ltd & Co Kg Engrenage à manchon en céramique
US11644012B2 (en) 2018-03-23 2023-05-09 Miba Gleitlager Austria Gmbh Wind turbine gearbox and method for producing a wind turbine gearbox

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB201705979D0 (en) * 2017-04-13 2017-05-31 Rolls Royce Plc A Gear, a method of manufacturing a gear and a geared gas turbine engine
EP3814654A4 (fr) * 2018-06-28 2021-12-08 ABB Schweiz AG Boîte de vitesses planétaire et articulation de robot associée et robot

Citations (6)

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Publication number Priority date Publication date Assignee Title
US3081648A (en) * 1958-12-11 1963-03-19 Gen Motors Corp Compound epicyclic gear mechanism
FR2661963A1 (fr) * 1990-05-14 1991-11-15 Niel Yves Reducteur de vitesse a train epicyclouidal.
DE102006029404A1 (de) 2006-06-27 2008-01-03 Daimlerchrysler Ag Zahnrad für ein Kraftfahrzeuggetriebe
DE102006030097B3 (de) * 2006-06-28 2008-02-14 Zf Friedrichshafen Ag Schraubrad
EP1967761A2 (fr) 2007-03-07 2008-09-10 Imk Automotive Gmbh Train épicycloïdal
DE102007063541A1 (de) * 2007-12-21 2009-07-02 Alfred Kärcher Gmbh & Co. Kg Antriebsvorrichtung für Hochdruckreinigungsgerät

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Publication number Priority date Publication date Assignee Title
DE102005009311A1 (de) * 2005-02-21 2006-08-24 Alfred Kärcher Gmbh & Co. Kg Hochdruckreinigungsgerät
JP5141339B2 (ja) * 2008-03-31 2013-02-13 オイレス工業株式会社 ブッシュ軸受及びそれを用いた自動車のラック−ピニオン式操舵装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3081648A (en) * 1958-12-11 1963-03-19 Gen Motors Corp Compound epicyclic gear mechanism
FR2661963A1 (fr) * 1990-05-14 1991-11-15 Niel Yves Reducteur de vitesse a train epicyclouidal.
DE102006029404A1 (de) 2006-06-27 2008-01-03 Daimlerchrysler Ag Zahnrad für ein Kraftfahrzeuggetriebe
DE102006030097B3 (de) * 2006-06-28 2008-02-14 Zf Friedrichshafen Ag Schraubrad
EP1967761A2 (fr) 2007-03-07 2008-09-10 Imk Automotive Gmbh Train épicycloïdal
DE102007063541A1 (de) * 2007-12-21 2009-07-02 Alfred Kärcher Gmbh & Co. Kg Antriebsvorrichtung für Hochdruckreinigungsgerät

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014208800A1 (de) * 2014-05-09 2015-11-12 Schaeffler Technologies AG & Co. KG Kunststoffplanetenrad mit eingespritztem Lager sowie Planetengetriebe
WO2016066745A3 (fr) * 2014-10-29 2016-06-23 Gwf Messsysteme Ag Roue et procédé de fabrication de cette roue
DE212015000257U1 (de) 2014-10-29 2017-06-20 Gwf Messsysteme Ag Rad
US10132648B2 (en) 2014-10-29 2018-11-20 Gwf Messsysteme Ag Wheel and method for producing the wheel
US11644012B2 (en) 2018-03-23 2023-05-09 Miba Gleitlager Austria Gmbh Wind turbine gearbox and method for producing a wind turbine gearbox
US20200088284A1 (en) * 2018-09-17 2020-03-19 Borgwarner Inc. Gear assembly having a gear comprising a first polymer and a bushing comprising a second polymer
CN109695697A (zh) * 2019-01-25 2019-04-30 上海创率复合材料有限公司 齿轮及齿轮制造方法
CN109695697B (zh) * 2019-01-25 2023-09-22 上海创率复合材料有限公司 齿轮及齿轮制造方法
WO2021069186A1 (fr) * 2019-10-09 2021-04-15 Rolls-Royce Deutschland Ltd & Co Kg Engrenage à manchon en céramique

Also Published As

Publication number Publication date
BR112013018724A2 (pt) 2016-10-25
EP2691673A1 (fr) 2014-02-05
CN103477122A (zh) 2013-12-25

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